WO2009087831A1 - 二重反転プロペラ式舶用推進装置 - Google Patents

二重反転プロペラ式舶用推進装置 Download PDF

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Publication number
WO2009087831A1
WO2009087831A1 PCT/JP2008/071641 JP2008071641W WO2009087831A1 WO 2009087831 A1 WO2009087831 A1 WO 2009087831A1 JP 2008071641 W JP2008071641 W JP 2008071641W WO 2009087831 A1 WO2009087831 A1 WO 2009087831A1
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WO
WIPO (PCT)
Prior art keywords
shaft
outer shaft
propeller
rotating
inner shaft
Prior art date
Application number
PCT/JP2008/071641
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
Hideki Shuto
Saiki Nishiyama
Original Assignee
Ihi Marine United Inc.
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Ihi Marine United Inc. filed Critical Ihi Marine United Inc.
Priority to EP08869724.8A priority Critical patent/EP2230171A4/en
Priority to BRPI0822155-3A priority patent/BRPI0822155A2/pt
Priority to KR1020107013243A priority patent/KR101255603B1/ko
Priority to CN200880124365.8A priority patent/CN101909986B/zh
Priority to US12/812,025 priority patent/US8585366B2/en
Publication of WO2009087831A1 publication Critical patent/WO2009087831A1/ja

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
    • B63H—MARINE PROPULSION OR STEERING
    • B63H5/00—Arrangements on vessels of propulsion elements directly acting on water
    • B63H5/07—Arrangements on vessels of propulsion elements directly acting on water of propellers
    • B63H5/08—Arrangements on vessels of propulsion elements directly acting on water of propellers of more than one propeller
    • B63H5/10—Arrangements on vessels of propulsion elements directly acting on water of propellers of more than one propeller of coaxial type, e.g. of counter-rotative type
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
    • B63H—MARINE PROPULSION OR STEERING
    • B63H23/00—Transmitting power from propulsion power plant to propulsive elements
    • B63H23/02—Transmitting power from propulsion power plant to propulsive elements with mechanical gearing
    • B63H23/10—Transmitting power from propulsion power plant to propulsive elements with mechanical gearing for transmitting drive from more than one propulsion power unit
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
    • B63H—MARINE PROPULSION OR STEERING
    • B63H5/00—Arrangements on vessels of propulsion elements directly acting on water
    • B63H5/07—Arrangements on vessels of propulsion elements directly acting on water of propellers
    • B63H5/08—Arrangements on vessels of propulsion elements directly acting on water of propellers of more than one propeller
    • B63H5/10—Arrangements on vessels of propulsion elements directly acting on water of propellers of more than one propeller of coaxial type, e.g. of counter-rotative type
    • B63H2005/106—Arrangements on vessels of propulsion elements directly acting on water of propellers of more than one propeller of coaxial type, e.g. of counter-rotative type with drive shafts of second or further propellers co-axially passing through hub of first propeller, e.g. counter-rotating tandem propellers with co-axial drive shafts
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
    • B63H—MARINE PROPULSION OR STEERING
    • B63H23/00—Transmitting power from propulsion power plant to propulsive elements
    • B63H23/32—Other parts
    • B63H23/321—Bearings or seals specially adapted for propeller shafts
    • B63H2023/323—Bearings for coaxial propeller shafts, e.g. for driving propellers of the counter-rotative type
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
    • B63H—MARINE PROPULSION OR STEERING
    • B63H23/00—Transmitting power from propulsion power plant to propulsive elements
    • B63H23/32—Other parts
    • B63H23/34—Propeller shafts; Paddle-wheel shafts; Attachment of propellers on shafts
    • B63H2023/346—Propeller shafts; Paddle-wheel shafts; Attachment of propellers on shafts comprising hollow shaft members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2300/00—Special features for couplings or clutches
    • F16D2300/06—Lubrication details not provided for in group F16D13/74
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2300/00—Special features for couplings or clutches
    • F16D2300/08—Details or arrangements of sealings not provided for in group F16D3/84
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
    • F16D3/18—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts the coupling parts (1) having slidably-interengaging teeth
    • F16D3/185—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts the coupling parts (1) having slidably-interengaging teeth radial teeth connecting concentric inner and outer coupling parts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/84—Shrouds, e.g. casings, covers; Sealing means specially adapted therefor

Definitions

  • the present invention relates to a counter-rotating propeller marine propulsion device.
  • a counter-rotating propeller is a propeller that achieves high propeller efficiency by recovering rotational energy flowing out from the front propeller to a propulsion force after being recovered by the propeller that rotates in the opposite direction to the front propeller.
  • a marine propulsion device equipped with a counter-rotating propeller is referred to as a “counter-rotating propeller marine propulsion device”.
  • the contra-rotating propeller marine propulsion device is disclosed in, for example, Patent Documents 1 and 2 below.
  • a “marine propulsion device” disclosed in Patent Document 1 is shown in FIG.
  • a marine vessel propulsion apparatus 100 has an inner shaft 102 and an outer shaft 101 arranged concentrically, a rear propeller 104 is attached to the inner shaft 102, a front propeller 103 is attached to the outer shaft 101,
  • the shaft 102 is rotationally driven by a main engine 105 such as a diesel engine or a gas turbine as a first drive device
  • the outer shaft 101 is rotationally driven by a main engine 106 such as a diesel engine or a gas turbine as a second drive device.
  • Reference numeral 107 denotes a drive shaft of the main engine 106
  • reference numeral 108 denotes a gear transmission device.
  • JP 2005-67436 A Japanese Unexamined Patent Publication No. 7-33084
  • the inner shaft is thinner and longer than the outer shaft, so it is possible to sufficiently absorb the influence of the hull displacement on the shaft center, but the outer shaft that is thicker than the inner shaft itself Therefore, it is difficult to sufficiently absorb the influence of the hull displacement on the shaft center.
  • the influence of the hull displacement on the axis of the outer shaft is not taken into consideration. Therefore, it is desired to solve such a problem.
  • the present invention has been made in view of the above problems, and an object of the present invention is to provide a counter-rotating propeller marine propulsion device that can eliminate the influence of the hull displacement on the axis of the outer shaft.
  • the contra-rotating propeller marine propulsion device of the present invention employs the following technical means.
  • the present invention has a hollow outer shaft attached to the hull with a front propeller attached to the rear end, and a rear propeller attached to the rear end to be supported rotatably inside the outer shaft.
  • a counter rotating thrust bearing that receives a thrust load from the outer shaft and transmits the thrust load to the inner shaft; and A thrust bearing for an inner shaft that receives the thrust load of the inner shaft and transmits the thrust load to the hull, and the power transmission device is disposed coaxially with the outer shaft and transmits a rotational driving force to the outer shaft.
  • the output shaft for the outer shaft and the outer shaft are Through Jo of flexible shaft coupling is connected, characterized in that.
  • the thrust load of the outer shaft is received by the inner shaft by the counter-rotating thrust bearing, the thrust load that combines the outer shaft and the inner shaft is received by the hull by the thrust bearing for the inner shaft, and the output for the outer shaft is received.
  • the rotational force of the shaft is transmitted to the outer shaft through the flexible shaft joint.
  • the thrust load of the outer shaft is not transmitted directly to the hull, but is transmitted only to the hull via the inner shaft, and the shaft center is allowed to be misaligned by the flexible shaft joint. The influence on the shaft center can be eliminated.
  • one or more drive devices may be provided.
  • the flexible shaft coupling is a gear coupling.
  • the gear coupling has a high allowable transmission torque and allows not only angular displacement but also axial displacement. Therefore, the gear coupling is extremely suitable as a shaft coupling for connecting the output shaft for the outer shaft and the outer shaft.
  • a hood that covers the gear coupling is provided on the stern side of the power transmission device, and lubricating oil is provided in the gear coupling.
  • At least one disk-shaped oil draining plate is provided and has a central opening into which the gear coupling is inserted, and prevents or suppresses leakage of lubricating oil from the gear coupling side to the engine room side. Is provided.
  • the gear coupling can be effectively lubricated, and leakage of lubricating oil to the engine room side can be prevented or suppressed.
  • an annular convex portion that protrudes radially outward and extends in the circumferential direction on the outer periphery of the gear coupling is axial.
  • the oil drain plate is disposed so that the inner peripheral end of the central opening is inserted between the two annular convex portions.
  • the labyrinth structure is formed by the oil drain plate and the annular convex portion, the leakage of the lubricating oil to the engine room side can be more effectively prevented.
  • the boss of the front propeller and the outer shaft which are configured as separate parts, are connected and fixed in the axial direction, and the front propeller
  • An annular recess is formed between the boss and the outer shaft, and the counter rotating thrust bearing is provided in the annular recess.
  • a counter rotating propeller unit can be constructed by incorporating a counter rotating thrust bearing and concentrically assembling it. For this reason, the assembly process in the engine room of the hull can be reduced by performing the process of incorporating the counter rotating thrust bearing before mounting the counter rotating propeller unit on the hull.
  • the drive device is a first drive device that is a rotation drive source of the outer shaft and a rotation drive source of the inner shaft.
  • the power transmission device is configured to transmit a rotational driving force of the first driving device and the second driving device to the outer shaft and the inner shaft independently of each other.
  • the outer shaft and the inner shaft are driven by independent drive sources, even if one of the drive sources fails, the front or rear propeller is driven by the other drive source. By doing so, the navigation of the ship can be continued.
  • the contra-rotating propeller marine propulsion device of the present invention it is possible to obtain an excellent effect that the influence of the hull displacement on the axis of the outer shaft can be eliminated.
  • FIG. 1 is a schematic plan view of a contra-rotating propeller marine propulsion device according to a first embodiment of the present invention.
  • FIG. 3 is an enlarged plan view around a gear coupling in FIG. 2.
  • FIG. 3 is an enlarged side view around a gear coupling in FIG. 2.
  • It is a schematic plan view of the contra-rotating propeller marine propulsion device according to the second embodiment of the present invention.
  • FIG. 2 is a schematic plan view of the contra-rotating propeller marine propulsion device 10A according to the first embodiment of the present invention.
  • a counter-rotating propeller marine propulsion device 10 ⁇ / b> A (hereinafter sometimes simply referred to as “propulsion device”) includes an outer shaft 11 to which a front propeller 13 is attached and an inner shaft to which a rear propeller 15 is attached. 12, a driving device 30 that is a rotational driving source of the outer shaft 11 and the inner shaft 12, and a power transmission device 20 ⁇ / b> A that transmits the rotational driving force of the driving device 30 to the outer shaft 11 and the inner shaft 12.
  • the outer shaft 11 is a hollow part and is installed through the stern tube 3 provided in the hull 2.
  • a front bush 5 and a rear bush 6 are provided between the stern tube 3 and the outer shaft 11, whereby the outer shaft 11 is rotatably supported by the hull 2.
  • a bow side stern tube sealing device 7 is provided on the end surface of the stern tube 3 on the bow side.
  • a stern side stern tube sealing device 8 is provided on the end surface of the stern tube 3 on the stern side.
  • a front propeller 13 is attached to the rear end of the outer shaft 11.
  • the front propeller 13 has a boss 13a at the center, and the bow side end face of the boss 13a and the stern side end face of the outer shaft 11 are connected and fixed by connecting means such as bolts.
  • An outer shaft sleeve shaft joint 16 is connected and fixed to the bow end of the outer shaft 11.
  • a hollow outer shaft intermediate shaft 17 is connected and fixed to the bow side end of the sleeve shaft joint 16 for outer shaft.
  • the outer shaft intermediate shaft 17 has a configuration that can be divided into a plurality of pieces (two or more) in the radial direction so that maintenance of accessory parts (such as the counter-rotating front seal device 37) of the inner shaft 12 can be performed.
  • the inner shaft 12 has a rear propeller 15 attached to the rear end thereof and is rotatably supported inside the outer shaft 11.
  • the rear propeller 15 has a boss 15 a at the center, is fitted to the rear end of the inner shaft 12 at the boss 15 a, and is fixed to the inner shaft 12 by a propeller nut 39.
  • a front radial bearing 35 and a rear radial bearing 36 are installed to rotatably support the inner shaft 12 with the outer shaft 11.
  • the front radial bearing 35 is disposed between the outer shaft sleeve coupling 16 and the inner shaft 12
  • the rear radial bearing 36 is configured such that the boss 13 a of the front propeller 13 and the inner shaft 12. It is arranged between.
  • the arrangement positions of the front radial bearing 35 and the rear radial bearing 36 are not limited to the positions described above, and may be, for example, between the front end portion and the rear end portion of the outer shaft 11 and the inner shaft 12.
  • a counter-rotating thrust bearing 40 that receives the thrust load of the outer shaft 11 and transmits it to the inner shaft 12 is disposed.
  • the counter rotating thrust bearing 40 is provided inside the boss of the front propeller 13. More specifically, an annular recess 14 is formed between the boss 13 a of the front propeller 13 and the outer shaft 11, and a counter rotating thrust bearing 40 is provided in the annular recess 14.
  • the counter rotating thrust bearing 40 may be a tilting pad type thrust bearing, for example.
  • a counter rotating lubricant is illustrated between the outer shaft 11 and the boss 13a of the front propeller 13 and the inner shaft 12. Not supplied from the counter-rotating lubricant supply device.
  • a counter-rotating front seal device 37 is disposed on the bow side end surface of the sleeve shaft joint 16 for the outer shaft, and on the stern side end surface of the boss 13a of the front propeller 13.
  • a counter-rotating rear seal device 38 is arranged.
  • the counter-rotating lubricating oil passes through the gap between the seal liner of the counter-rotating rear seal device 38 and the inner shaft 12 after lubricating the rear radial bearing 36 and passes through the boss 15a of the rear propeller 15. It passes through the oil hole 50, passes through the inside of the propeller cap 51 attached to the rear end portion of the boss 15 a, enters the hollow portion of the inner shaft 12, and is provided at the bow-side end portion of the shaft of the inner shaft output main gear 29. It passes through the sealing device 47 and is returned to a lubricating oil tank (not shown) installed in the engine room. The opening at the tip of the shaft of the inner shaft output main gear 29 is closed by a stop flange 52.
  • the second drive device 32 includes a first drive device 31 that is a rotation drive source of the outer shaft 11 and a second drive device 32 that is a rotation drive source of the inner shaft 12.
  • the first drive device 31 and the second drive device 32 may be a main engine such as a gas turbine engine or a diesel engine, or may be an electric motor.
  • an electric motor for example, one or a plurality of gas turbine generators or diesel generators can be mounted in an engine room and used as a power source.
  • the power transmission device 20A employed in the configuration example of FIG. 2 is configured to transmit the rotational driving force of the first driving device 31 and the second driving device 32 to the outer shaft 11 and the inner shaft 12 independently.
  • This is a counter-rotating gear transmission device.
  • the power transmission device 20 ⁇ / b> A includes a housing 21, and includes an outer shaft transmission mechanism 18 ⁇ / b> A and an inner shaft transmission mechanism 18 ⁇ / b> B inside the housing 21.
  • the outer shaft transmission mechanism 18A and the inner shaft transmission mechanism 18B are both constituted by a gear transmission mechanism.
  • the outer shaft transmission mechanism 18A is arranged coaxially with the output shaft 31a of the first driving device 31 and is coaxial with the outer shaft 11 and the outer shaft input gear 22 to which the driving force from the first driving device 31 is inputted. Between the outer shaft input gear 22 and the outer shaft output main gear 24.
  • the hollow outer shaft output main gear 24 is an outer shaft output shaft that transmits rotational driving force to the outer shaft 11. And an intermediate small gear 23 for the outer shaft.
  • the output shaft 31a of the first drive device 31 and the outer shaft input gear 22 are connected via a gear coupling 33a so as to be able to absorb errors during installation and changes in the shaft center due to hull displacement.
  • the number of outer intermediate small gear 23 is one, but there may be a plurality.
  • the inner shaft transmission mechanism 18B is disposed coaxially with the output shaft 32a of the second drive device 32, and receives the drive force from the second drive device 32, and the outer shaft output shaft 24.
  • the inner shaft output main gear 29 which is inserted coaxially with the inner shaft 12 and transmits the rotational driving force to the inner shaft 12, the inner shaft input gear 27 and the inner shaft output.
  • An intermediate small gear 28 for an inner shaft disposed between the main gear 29 and the main gear 29.
  • the output shaft 32a of the second drive device 32 and the inner shaft input gear 27 are connected via a gear coupling 33b so as to absorb errors during installation and changes in the shaft center due to hull displacement.
  • there is one intermediate small gear 28 for the inner shaft but a plurality of intermediate small gears 28 may be provided.
  • the inner shaft output main gear 29 and the inner shaft 12 are connected and fixed by a sleeve shaft joint 26 for inner shaft.
  • an inner shaft thrust bearing 41 that receives a thrust load from the inner shaft 12 (a load combining the thrust load of only the inner shaft 12 and the thrust load of only the outer shaft 11) and transmits it to the hull 2 is disposed. ing.
  • the inner shaft thrust bearing 41 is provided on the bow side portion of the housing 21 of the power transmission device 20. For this reason, the thrust load from the inner shaft 12 is supported by the hull 2 via the housing 21.
  • the arrangement position of the inner shaft thrust bearing 41 is not limited to the above-described position as long as the thrust load from the inner shaft 12 can be transmitted to the hull 2. Therefore, as long as it is on the bow side of the output shaft 24 for the outer shaft, it may be inside the housing 21 or outside the housing 21.
  • both the outer shaft transmission mechanism 18A and the inner shaft transmission mechanism 18B are gear transmission mechanisms, but one or both are other transmission mechanisms (belt transmission mechanism, chain transmission mechanism, etc.). Also good.
  • the outer shaft transmission mechanism 18A and the inner shaft transmission mechanism 18B are housed in the single housing 21, but may be housed in separate housings 21.
  • the outer shaft output main gear 24 and the outer shaft 11 are connected via a hollow flexible shaft joint 19.
  • the flexible shaft joint 19 is a gear coupling 19A
  • the output main gear 24 for outer shaft is connected and fixed to the bow side of the gear coupling 19A
  • the outer shaft intermediate shaft 17 is gear coupling. It is fixedly connected to the stern side of 19A. Accordingly, the rotational driving force of the outer shaft output main gear 24 is transmitted to the outer shaft 11 via the gear coupling 19A, the outer shaft intermediate shaft 17 and the outer shaft sleeve shaft coupling 16.
  • the flexible shaft joint 19 may be a flange-type flexible shaft joint or a roller chain shaft joint, but a gear coupling 19A that has a high allowable transmission torque and can allow not only angular displacement but also axial displacement is suitable. It is.
  • an outer shaft short-circuit device 49 is provided on the outer shaft intermediate shaft 17.
  • the shaft of the inner shaft output main gear 29 protrudes from the bow end of the housing 21, and the inner shaft short-circuit device 48 is provided at this portion. Is provided.
  • FIG. 3 and 4 are enlarged views around the gear coupling 19A in FIG. 2, FIG. 3 is a schematic plan view, and FIG. 4 is a schematic side view.
  • the gear coupling 19A employed in this configuration example includes a first inner cylinder 19a provided on the bow side, a second inner cylinder 19b provided on the stern side, a first inner cylinder 19a and a second inner cylinder. And an outer cylinder 19c surrounding 19b.
  • the rotational driving force of the output main gear 24 for the outer shaft absorbs axial displacement, angular displacement and parallel displacement of the shaft center, and transmits it to the outer shaft 11 side.
  • a gear coupling 19A composed of two inner cylinders 19a, 19b and one outer cylinder 19c is employed, but a gear cup composed of one inner cylinder and one outer cylinder. A ring may be employed. Also with this form of gear coupling, axial displacement and angular displacement of the shaft center can be absorbed.
  • the first driving device 31 when the first driving device 31 is rotationally driven, the driving force is transmitted to the outer shaft 11 via the outer shaft transmission mechanism 18A, the gear coupling 19A, and the like before being attached to the outer shaft 11.
  • the propeller 13 rotates.
  • the second driving device 32 when the second driving device 32 is driven to rotate, the driving force is transmitted to the inner shaft 12 via the inner shaft transmission mechanism 18B and the inner shaft sleeve shaft joint 26, and is attached to the inner shaft 12 after the propeller. 15 rotates.
  • the front propeller 13 and the rear propeller 15 are rotated in opposite directions by rotating the outer shaft 11 and the inner shaft 12 in opposite directions.
  • the rotational direction of the first and second drive units 31 and 32 for rotating the front propeller 13 and the rear propeller 15 in opposite directions depends on the configuration of the power transmission device 20, but the configuration example of FIG. In this case, if the rotation directions of the output shafts of the first driving device 31 and the second driving device 32 are opposite to each other, the front propeller 13 and the rear propeller 15 rotate in opposite directions.
  • lubricating oil 45 is supplied into the housing 21 to lubricate the outer shaft transmission mechanism 18A, the inner shaft transmission mechanism 18B, and the gear coupling 19A.
  • a hood 21a covering the gear coupling 19A is provided on the stern side of the housing 21.
  • the housing 21 and the hood 21a communicate with each other, and lubricating oil is supplied from the housing 21 side to the gear coupling 19A in the hood 21a.
  • the hood 21 a may be formed integrally with the housing 21 or may be configured as a separate part from the housing 21.
  • an oil drain plate 42 having a circular center opening is provided in the hood 21a in the vicinity of the outer periphery of the first inner cylinder 19b of the gear coupling 19A in order to prevent the lubricating oil from leaking to the engine room side. .
  • Two annular convex portions 43 protruding outward in the radial direction and extending over the entire circumference in the circumferential direction are provided apart from each other in the axial direction on the outer periphery of the second inner cylinder 19b.
  • the oil drain plate 42 is disposed so that the inner peripheral end of the circular central opening is inserted between the two annular convex portions 43. With this configuration, the lubricating oil 45 is prevented from leaking from the gear coupling 19A side to the engine room side.
  • Three or more annular protrusions 43 are provided apart in the axial direction, and two or more oil drain plates 42 are provided. The inner peripheral edge of the circular central opening of each oil drain plate 42 is between the annular protrusions 43, respectively.
  • the oil leakage prevention function may be further enhanced by being configured to be inserted.
  • the lubricating oil 45 enters from between the outer cylinder 19c and the first inner cylinder 19a (position A in FIG. 4), and the gear coupling 19A and the inner shaft 12 are inserted. And enters and accumulates in the outer shaft intermediate shaft 17.
  • the lubricating oil 45 accumulated inside the outer shaft intermediate shaft 17 rotates together with the outer shaft intermediate shaft 17 and sticks to the inner surface of the outer shaft intermediate shaft 17 by centrifugal force at that time, but the storage capacity of the outer shaft intermediate shaft 17 is increased.
  • the excess amount of the lubricating oil 45 overflows from the circular opening provided on the bow side of the outer shaft intermediate shaft 17, it is like a hollow cylinder having an inner peripheral surface with the position indicated by the symbol H in the figure as the liquid level It becomes.
  • the lubricating oil 45 overflowed from the outer intermediate shaft 17 returns to the gear coupling 19A side, passes through the space between the outer cylinder 19c, the first inner cylinder 19a, and the second inner cylinder 19b, and is discharged from the outlet 46, not shown. Returned to the lubricating oil tank.
  • the above-described liquid surface position H of the lubricating oil 45 is a position where the counter-rotating front seal device 37 can be lubricated, and is provided on the front side of the outer intermediate shaft 17 so that the lubricating oil 45 is accumulated up to such a position.
  • the size of the opening diameter of the circular opening is set.
  • the thrust load of the outer shaft 11 is received by the inner shaft 12 by the counter-rotating thrust bearing 40, and the thrust load obtained by combining the outer shaft 11 and the inner shaft 12 by the inner shaft thrust bearing 41 is received by the hull 2.
  • the rotational force of the output shaft 24 is transmitted to the outer shaft 11 via the gear coupling 19 ⁇ / b> A that is the flexible shaft joint 19.
  • the thrust load of the outer shaft 11 is not transmitted directly to the hull 2, but is transmitted to the hull 2 only through the inner shaft 12, and the deflection of the shaft center is allowed by the flexible shaft joint 19,
  • the influence of the hull displacement on the axis of the outer shaft 11 can be eliminated.
  • the gear coupling 19A that allows not only angular displacement but also axial displacement is employed as the flexible shaft coupling 19, the influence of the hull displacement on the shaft center of the outer shaft 11 is effective. Can be eliminated.
  • any one of the drive sources (for example, the first drive device 31). ) Can be continued by driving the front propeller 13 or the rear propeller 15 by the other drive source (for example, the second drive device 32).
  • FIG. 5 is a schematic plan view of a contra-rotating propeller marine propulsion device 10B according to the second embodiment of the present invention. This embodiment is different from the first embodiment with respect to the drive device 30 and the power transmission device 20B. Although FIG. 5 which shows this embodiment is simplified with respect to FIG. 2 which shows 1st Embodiment, about parts other than the drive device 30 and the power transmission device 20B, it is the same as 1st Embodiment.
  • the power transmission device 20B rotates biaxially in directions opposite to each other with respect to a uniaxial rotational input. Is a counter-rotating transmission device. That is, the power transmission device 20B converts the rotational driving force of the driving device into the driving force in the rotation direction opposite to each other, and transmits it to the outer shaft 11 and the inner shaft 12, respectively.
  • the output shaft for the outer shaft of the power transmission device 20B is transmitted to the outer shaft 11 through the gear coupling 19A as in the first embodiment.

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  • Chemical & Material Sciences (AREA)
  • Engineering & Computer Science (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • Ocean & Marine Engineering (AREA)
  • Gear Transmission (AREA)
PCT/JP2008/071641 2008-01-08 2008-11-28 二重反転プロペラ式舶用推進装置 WO2009087831A1 (ja)

Priority Applications (5)

Application Number Priority Date Filing Date Title
EP08869724.8A EP2230171A4 (en) 2008-01-08 2008-11-28 SHIP DRIVE WITH ROTATION PROPELLER
BRPI0822155-3A BRPI0822155A2 (pt) 2008-01-08 2008-11-28 Dispositivo de propulsão marítimo com propulsor de contra-rotação
KR1020107013243A KR101255603B1 (ko) 2008-01-08 2008-11-28 이중 반전 프로펠러식 선박용 추진 장치
CN200880124365.8A CN101909986B (zh) 2008-01-08 2008-11-28 双反转螺旋桨式船用推进装置
US12/812,025 US8585366B2 (en) 2008-01-08 2008-11-28 Contra-rotating propeller marine propulsion device

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US8585366B2 (en) 2013-11-19
KR20100096176A (ko) 2010-09-01
JP2009161050A (ja) 2009-07-23
EP2230171A4 (en) 2014-10-29
JP5266542B2 (ja) 2013-08-21
KR101255603B1 (ko) 2013-04-16
CN101909986B (zh) 2014-01-08
BRPI0822155A2 (pt) 2015-06-16
US20110033296A1 (en) 2011-02-10
EP2230171A1 (en) 2010-09-22

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